US9086145B2 - Clamping force generator - Google Patents
Clamping force generator Download PDFInfo
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- US9086145B2 US9086145B2 US13/765,409 US201313765409A US9086145B2 US 9086145 B2 US9086145 B2 US 9086145B2 US 201313765409 A US201313765409 A US 201313765409A US 9086145 B2 US9086145 B2 US 9086145B2
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- traction ring
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/664—Friction gearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
- F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
- F16H15/04—Gearings providing a continuous range of gear ratios
- F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
- F16H15/26—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a spherical friction surface centered on its axis of revolution
- F16H15/28—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a spherical friction surface centered on its axis of revolution with external friction surface
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
- F16H15/48—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members with members having orbital motion
- F16H15/50—Gearings providing a continuous range of gear ratios
- F16H15/52—Gearings providing a continuous range of gear ratios in which a member of uniform effective diameter mounted on a shaft may co-operate with different parts of another member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
- F16H25/186—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions with reciprocation along the axis of oscillation
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/18—Mechanical movements
- Y10T74/18056—Rotary to or from reciprocating or oscillating
- Y10T74/18296—Cam and slide
- Y10T74/18304—Axial cam
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/18—Mechanical movements
- Y10T74/18056—Rotary to or from reciprocating or oscillating
- Y10T74/18296—Cam and slide
- Y10T74/18304—Axial cam
- Y10T74/18312—Grooved
Definitions
- the field of the invention relates generally to mechanical power transmissions, and more particularly the invention pertains to devices and methods relating to generating clamping force in certain types of said transmissions.
- Certain transmissions for example some continuously or infinitely variable transmissions, often include one or more mechanisms for generating a clamping force that facilitates the transmission of torque between or among transmission components via traction or friction.
- Some clamping force generators are referred to as axial force generators (AFGs) because, typically, the clamping force produced by the AFGs resolves (or must be reacted) along a main or longitudinal axis of a transmission.
- AFGs axial force generators
- One known method of generating clamping force is to place rollers between a set of load cams (or load ramps) and a reacting surface, such as for example another set of load cams or a flat driven or driving surface. As the relative motion between the opposing surfaces drives the rollers up the ramps, the rollers act to push apart the opposing surfaces. Since the opposing surfaces are typically substantially constrained to react the pushing of the rollers, a clamping force arises in the assembly. The clamping force is then usually transmitted to tractive or frictional torque transmission components.
- FIG. 1 is a cross-section of an exemplary continuously variable transmission (CVT) that uses a clamping force generation mechanism (CFG).
- CVT continuously variable transmission
- CFG clamping force generation mechanism
- FIG. 2 is a detailed view A of the CVT of FIG. 1 .
- FIG. 3 is an exploded assembly view of certain components of a CFG that can be used in the CVT of FIG. 1 .
- FIG. 4 is an exploded assembly view of another CFG, which can be used in transmissions such as the CVT of FIG. 1 .
- FIG. 5 is a perspective view of the CFG of FIG. 4 .
- FIG. 6 is a second perspective view of the CFG of FIG. 4 .
- FIG. 7 is an exploded assembly view of yet another CFG.
- FIG. 8 is an exploded assembly view of still another CFG.
- FIG. 9A is a cross-sectioned, exploded assembly view of a CFG having spring loaded ramps.
- FIG. 9B is a cross-sectional view of the CFG of FIG. 9A .
- FIG. 9C is a cross-sectional view of another CFG having spring loaded ramps.
- FIG. 9D is a cross-sectional view of still another CFG having spring loaded ramps.
- FIG. 10A is a partially sectioned, perspective view of yet a different CFG that can be used in a CVT.
- FIG. 10B is a partially sectioned, exploded assembly view of the CFG of FIG. 10A .
- FIG. 10C is a partially cross-sectioned and exploded assembly view of the CFG of FIG. 10A .
- FIG. 10D is a detailed view B of the CFG of FIG. 10A .
- FIG. 11A is an exploded assembly view of yet one more CFG, which can be used in transmissions such as the CVT of FIG. 1 .
- FIG. 11B is a partially sectioned, perspective view of yet another CFG.
- FIG. 11C is a perspective view of yet another CFG.
- FIG. 12 is a partially sectioned, perspective view of another CFG, which can be used in transmissions such as the CVT of FIG. 1 .
- FIG. 13A is a perspective view of another CFG, which can be used in transmissions such as the CVT of FIG. 1 .
- FIG. 13B is a detail view C 1 of certain components of the CFG of FIG. 13A .
- FIG. 13C is a cross-sectional view of certain components of another CFG.
- FIG. 13D is a cross-sectional view of certain components of another CFG.
- FIG. 13E is a cross-sectional view of certain components of yet another CFG.
- FIG. 13F is a cross-sectional view of certain components of a different CFG.
- FIG. 14A is a partially sectioned, perspective view of yet another CFG which can be used in transmissions such as the CVT of FIG. 1 .
- FIG. 14B is a cross-sectional view of certain components of the CFG of FIG. 14A .
- FIG. 15A is a partially sectioned, perspective view of yet another CFG which can be used in transmissions such as the CVT of FIG. 1 .
- FIG. 15B is a cross-sectional view of certain components of the CFG of FIG. 15A .
- FIG. 16A is an exploded and partially sectioned view of a CFG that can be used with the CVT of FIG. 1 .
- FIG. 16B is a detail view of the CFG of FIG. 16A .
- FIG. 17A is an assembly and partially sectioned view of yet another CFG that can be used with a CVT.
- FIG. 17B is a Detail D view of the CFG of FIG. 17A .
- the terms “operationally connected,” “operationally coupled”, “operationally linked”, “operably connected”, “operably coupled”, “operably linked,” and like terms refer to a relationship (mechanical, linkage, coupling, etc.) between elements whereby operation of one element results in a corresponding, following, or simultaneous operation or actuation of a second element. It is noted that in using said terms to describe inventive embodiments, specific structures or mechanisms that link or couple the elements are typically described. However, unless otherwise specifically stated, when one of said terms is used, the term indicates that the actual linkage or coupling may take a variety of forms, which in certain instances will be readily apparent to a person of ordinary skill in the relevant technology.
- axial As used here, the terms “axial,” “axially,” “lateral,” “laterally,” refer to a position or direction that is coaxial or parallel with a longitudinal axis of a transmission or variator.
- radial and “radially” refer to locations or directions that extend perpendicularly from the longitudinal axis. For clarity and conciseness, at times components labeled similarly (for example, spring 112 A and spring 112 B) will be referred to collectively by a single label (for example, springs 112 ).
- FIG. 1 it illustrates a spherical-type CVT 50 that can be used to change the ratio of input speed to output speed.
- the CVT 50 has a main axle 52 extending through the center of the CVT 50 .
- the main axle 52 provides axial and radial positioning and support for other components of the CVT 50 .
- the main axle 52 defines a longitudinal axis of the CVT 50 that will serve as a reference point for describing the location and or motion of other components of the CVT 50 .
- the CVT 50 includes a hub shell 54 that couples to a hub cover 56 .
- the hub shell 54 and the hub cover 56 forms a housing.
- the CVT 50 includes a number of power rollers 58 arranged angularly about the main axle 52 and placed in contact with an input traction ring 60 , an output traction ring 62 , and a support member 64 .
- Legs 66 couple to power roller axles 68 , which provide tiltable axes of rotation for the power rollers 58 .
- the tilting of the power roller axles 68 causes the radii (relative to the power roller axles 68 ) at the point of contact between the power rollers 58 and the traction rings 60 , 62 to change, thereby changing the speed ratio of output speed to input speed.
- Embodiments of the CVT 50 often use a clamping force generation mechanism (clamping force generator or CFG) to prevent slip between the power rollers 58 and the traction rings 60 , 62 when transmitting certain levels of torque.
- clamping force generation includes providing preloading, such as by way of one or more of an axial spring (for example, a wave spring); a torsion spring, a compression coil spring, or a tension coil spring.
- the CVT 50 includes an input-side clamping force generation subassembly 70 (CFG 70 ) as shown in detail view A.
- CFG 70 includes a cam driver 72 in contact with a number of load cam rollers 74 .
- the load cam rollers 74 are positioned and supported by a roller cage 76 .
- the load cam rollers 74 also contact a set of ramps 106 that are, in this embodiment, integral with the input traction ring 60 .
- the cam driver 72 rotates about the main axle 52 , the cam driver 72 causes the load cam rollers 74 to ride up the ramps 106 .
- This roll-up action energizes the load cam rollers 74 and thereby generates a clamping force, as the load cam rollers 74 are compressed between the cam driver 72 and the ramps 106 .
- the clamping force serves to urge the input traction ring 60 against the power rollers 58 .
- the roller cage 76 includes a roller retainer ring 78 adapted to receive and retain the load cam rollers 74 .
- the roller retainer ring 78 transitions into a retainer extension 80 , which is a generally annular ring extending from the roller retaining ring 78 at an angle of about 90 degrees.
- the roller retainer extension 80 in some embodiments, is adapted to pilot on the traction ring 60 to, in part, aid in retaining a torsion spring 82 in a spring groove 104 of the traction ring 60 .
- the retainer extension 80 includes a retaining slit 84 for receiving and retaining an end of the torsion spring 82 .
- the depth of the spring groove 104 , the pitch diameter of the torsion spring 82 in its free state, the length and wire diameter of the torsion spring 82 , and the internal diameter of the retainer extension 80 are selected such that expansion of the torsion spring 82 in the spring groove 104 is constrained by the retainer extension 80 so that a partially wound torsion spring 82 biases the roller cage 76 to cause the load cam rollers 74 to roll up the ramps 106 and come to rest on or near a substantially flat portion 107 of the traction ring 60 .
- the roller cage 76 Upon assembly of the CVT 50 , the roller cage 76 is turned relative to the traction ring 60 , thereby winding the torsion spring 82 until the load cam rollers 74 come to rest substantially at a bottom portion 109 of the ramps 106 .
- This assembly process ensures, among other things, that the torsion spring 82 is preloaded to bias the load cam rollers 74 up the ramps 106 so that the load cam rollers 74 are properly staged for activation during operation of the CVT 50 . Additionally, this component configuration and assembly process facilitates the take up of stack up tolerances present during assembly of the CVT 50 .
- the input CFG 70 and an output CFG 71 are used.
- the torsion springs 82 , 83 act upon, respectively, the input traction ring 60 and the roller cage 76 , and the output traction ring 84 and the roller cage 77 (see FIG. 1 ), to provide a certain amount of clamping of the traction rings 60 , 62 against the power rollers 58 .
- the retainer extension 80 of the roller cage 76 interacts with the traction ring 60 and/or the torsion spring 82 to produce an undesired drag force in the CVT 50 .
- the clamping force generation mechanisms described below generally reduce or eliminate the potential for generating the drag force.
- a CFG 100 can include a traction ring 102 having a spring groove 104 and a set of ramps 106 .
- the CFG 100 includes a roller cage 108 that holds and supports a group of load cam rollers 74 , which can be cylindrical rollers, spherical rollers, or barrel-shaped rollers, for example.
- the roller cage 108 can be fitted with an extension or flange 109 that fits over an outer diameter 103 of the traction ring 102 .
- the CFG 100 includes one or more of springs 112 and wires 114 . As shown in FIG. 5 , the springs 112 and the wires 114 are placed in the spring groove 104 .
- the springs 112 can be coil springs of the compression or tension type, for example.
- one end of the spring 112 A couples to the traction ring 102 via a dowel pin 116 A, which is inserted through suitable holes in the traction ring 102 .
- the other end of the spring 112 A couples to one end of the wire 114 A.
- another end of the wire 114 A is provided with a bend or hook 118 A configured to engage a tab 120 A of the roller cage 108 .
- the CFG 100 includes a stop pin 122 suitably configured to engage the tab 120 A at a tab notch 124 (see FIG. 4 ).
- the traction ring 102 can be provided with a hole 126 for receiving and supporting the stop pin 122 .
- the spring 112 B couples to the wire 114 B and, via a dowel pin 116 B, to the traction ring 102 .
- a hook 118 B of the wire 114 B engages the tab 120 B.
- a CFG 400 can include the traction ring 102 and the roller cage 108 , as well as other components of the CFG 100 .
- the CFG 400 uses springs 402 instead of the springs 112 and the wires 114 .
- FIG. 8 shows yet another embodiment of a CFG 500 that uses relatively short spring 502 instead of the longer springs 402 .
- the CFGs 100 , 400 , and 500 are assembled and operated in substantially the same manner as already described above with reference to the CFG 70 .
- the springs 112 and the stop pin 122 are configured such that the springs 112 bias the roller cage 108 and the load cam rollers 74 to be initially staged at or in the vicinity of the flat surfaces 107 of the traction ring 102 .
- the roller cage 108 is rotated so that the load cam rollers 74 are positioned substantially at the bottom portion 109 of the ramps 106 .
- the springs 112 will then act upon the roller cage 108 to cause the load cam rollers 74 to roll back up the ramps 106 for some distance to produce a preload that ensures that a certain minimum level of clamping force will be always available during operation of the CVT 50 .
- the springs 114 , 402 , and 502 of some embodiments are made of any resilient material capable of being formed into a spring
- the springs 114 , 402 , and 502 are made of, for example, metal, rubber, composite, plastic, etc.
- the springs 114 are general use extension springs such as spring SP-9606 distributed by Prime-Line Product Company of San Bernardino, Calif., USA.
- the spring SP-9606 has a length of about 2.5 inches, an outer diameter of about 5/32′′, and wire diameter of about 0.02 inches.
- the springs 114 have a load capacity of about 1.5 to 3.5 pounds.
- the wires 114 are made of a metallic material; however, in other embodiments, the wires 114 are made any other suitable material, such as rubber, composite, plastic, etc.
- a CFG 600 can include a cam base ring 602 , a traction ring 604 , and a number of spring loaded ramps 606 in contact with load cam rollers 601 .
- the load cam rollers 601 are arranged and retained in a cam roller cage 622 .
- the cam roller cage 622 is substantially similar to the cam roller cage 76 .
- a portion of the spring loaded ramps 606 can be retained in, supported by, and/or reacted by the cam roller cage 622 by, for example, a slot 630 of the cam roller cage 622 .
- the cam base ring 602 can be an annular ring similar to, for example, the cam driver 72 .
- a number of torque transferring shoulders 608 can be arranged on the cam base ring 602 and couple one end of the spring loaded ramps 606 .
- a number of springs 610 can be arranged on the cam base ring 602 so that one end of the spring loaded ramps 606 is coupled to the springs 610 .
- the torque transferring shoulder 608 couples to one end of the spring loaded ramp 606 and the spring 610 couples to the other end of the spring loaded ramp 606 .
- the springs 610 can be coil springs of the compression type, for example.
- the spring loaded ramp 606 can be configured to have a profile substantially similar to the ramps 106 and have, for example, a flat surface 609 in contact with cam roller 601 .
- the spring loaded ramp 606 can be made from hardened steel, powdered metal, or other suitable material for withstanding the loads and stresses imposed on the CFG 600 during operation of CVT 50 .
- the torque transferring shoulders 608 can be integral to the cam base ring 602 or, for example, be formed with dowels pressed into bores or slots such as bores 618 on the cam base ring 602 . The latter may accommodate alternative manufacturing processes.
- springs 610 can be retained in pockets or bores, such as bores 619 formed in the cam base ring 602 .
- the cam base ring 602 can further include inner and outer shoulders 620 and 621 respectively for, among other things, retaining the spring loaded ramps 606 .
- the springs 610 motivate the spring loaded ramps 606 to engage the load cam rollers 601 so that a cam roller 601 is positioned substantially at the flat surface 609 of a respective spring loaded ramp 606 .
- the spring 610 is configured to actuate the spring loaded ramp 606 to cause the load cam roller 601 to roll up the spring loaded ramp 606 for some distance to produce a preload that ensures that a certain minimum level of clamping force will be available during operation of the CVT 50 .
- input torque is delivered to the cam base ring 602 .
- the torque transferring shoulders 608 deliver the input torque to the spring loaded ramps 606 .
- the spring loaded ramp 606 tends to wedge between the torque transferring shoulder 608 and, the load cam roller 601 .
- the spring 610 can facilitate, among other things, the wedging action of the spring loaded ramp 606 .
- the load cam roller cage 622 that is coupled to the load cam roller 601 and the spring loaded ramp 606 can be configured to prevent the load cam roller 601 from decoupling from the spring loaded ramp 606 during a free-wheeling or back-driving condition.
- a CFG 615 includes springs 611 that can be used instead of springs 610 .
- the springs 611 can be scissor springs of the compression type, for example, and can be attached to the cam base ring 602 .
- the springs 610 can be wave springs (not shown) of the compression type, for example, and can be retained in radial slots (not shown) instead of bores 619 formed into the cam base ring 602 .
- a CFG 617 uses a set of magnetic elements 614 A and 614 B, wherein the magnetic element 614 A can be arranged in a substantially similar manner as the springs 610 and the magnetic element 614 B can be attached to one end of the spring loaded ramp 606 so that the resultant force generated between the magnetic elements 614 A, 614 B provides the desired preload force on the spring loaded ramp 606 .
- a CFG 700 can include a traction ring 702 , a cam driver 704 , and a load cam roller cage 706 in cooperation with a plurality of load cam rollers 708 .
- the traction ring 702 can be formed with a plurality of ramps 703 .
- the cam driver 704 can be formed with a plurality of ramps 705 .
- the ramps 703 and 705 are substantially similar to ramps 106 and are arranged to contact the load cam rollers 708 .
- the load cam rollers 708 are retained in the load cam roller cage 706 that functions substantially similar to cage 76 .
- a plurality of springs 710 can be retained in the load cam roller cage 706 and can be arranged to contact the cam driver 704 and the traction ring 702 .
- the cam driver 704 can be provided with radial splines 730 and slots 732 .
- the splines 730 and slots 732 function to, among other things, mate with an input coupling provided on the CVT 50 that is generally of the kind disclosed previously.
- the load cam roller cage 706 includes a first slotted ring 706 A coupled to a second slotted ring 706 B.
- the first and second slotted rings 706 A, 706 B are received in a band 706 C.
- the first slotted ring 706 A and the second slotted ring 706 B can be provided with slots 799 .
- the first slotted ring 706 A and the second slotted ring 706 B can be coupled together with, for example, a plurality of pegs 707 A and bores 707 B.
- each of the slotted rings 706 has equally as many pegs 707 A as bores 707 B.
- the arrangement of the pegs 707 A and the bores 707 B around the face of the slotted rings 706 can be configured to accommodate various manufacturing methods, such as plastic injection molding.
- the arrangement of the pegs 707 A and the bores 707 B can allow the slotted rings 706 to be substantially identical for manufacture while retaining features for alignment during assembly.
- the pegs 707 A are arranged around half the circumference of the slotted ring 706 while the bores 707 B are arranged around the other half of the circumference so that once assembled the slotted rings 706 A and 706 B are aligned when joined.
- the slotted rings 706 A and 706 B are further retained around their outer circumference or periphery with the band 706 C.
- the band 706 C can be a generally annular ring made from, for example, steel or aluminum.
- An outer circumference of the band 706 C can have a number of protrusions 750 and 751 .
- the protrusions 750 and 751 are generally aligned with the slotted rings 706 A and 706 B.
- the protrusions 750 and 751 are configured to, among other things, axially retain and align the slotted rings 706 A and 706 B. It will be readily apparent to a person of ordinary skill in the relevant technology that the load cam roller cage 706 can be used in various applications in the same manner as the cage 76 , the cage 108 , or the cage 622 .
- a plurality of springs 710 are retained in load cam roller cage 706 and are arranged in such a way that one end of the spring 710 couples to the cam driver 704 and the other end of the spring 710 couples to the traction ring 702 .
- the springs 710 can be generally arranged 180-degrees with respect to each other for configurations provided with two springs.
- a middle portion of the spring 710 is retained in the load cam roller cage 706 .
- Shoulders 740 and 742 formed on the slotted rings 706 A and 706 B, respectively, can be provided to capture the middle portion of the spring 710 .
- the spring 710 can be a coil spring of the compression type.
- the spring 710 can be a wire spring. In yet other embodiments, the spring 710 can be a flat spring. It is preferable that the ends of spring 710 have rounded or curved surfaces that have generally the same shape as reaction surfaces 715 and 721 .
- a groove 714 can be formed onto the cam driver 704 .
- a groove 720 can be formed onto the traction ring 702 . Once assembled, the grooves 714 and 720 aid to, among other things, retain the spring 710 and provide the reaction surfaces 715 and 721 , respectively. Channels 716 and 718 can be formed into the slotted rings 706 A and 706 B to provide clearance for the spring 710 .
- the springs 710 are configured to apply a force on the cam driver 704 and the traction ring 702 that engages the load cam rollers 708 with the cam driver 704 and the traction ring 702 .
- the load cam rollers 708 are positioned generally on the flat portion of the ramps 703 and 705 .
- the interaction between the traction ring 702 , the cam driver 704 , and the springs 710 causes the cam rollers 708 to roll up the ramps 703 and 705 for some distance to produce a preload that ensures that a certain minimum level of clamping force will be available during operation of the CVT 50 .
- a CFG 800 can include the traction ring 102 and the load cam roller cage 108 , as well as other components of the CFG 100 .
- the CFG 800 uses magnets 802 and 822 instead of the springs 112 and the wires 114 .
- Magnet 802 A can be attached to the tab 120 A while the magnet 822 A can be attached at the bore 126 A so that the arrangement of the magnetic poles on the magnet 802 A and the magnet 822 A provides the desired resultant force between the traction ring 102 and the roller cage 108 in a substantially similar manner as the springs 112 and wire 114 .
- the magnetic elements 802 and 822 can have different shapes and, consequently, the shapes shown are merely an example.
- the magnets 802 and 822 energize the roller cage 108 and consequently move the load cam rollers 74 up the ramps 106 to produce a preload that ensures a certain minimum level of clamping force during operation of the CVT 50 .
- a CFG 900 can include a traction ring 902 , cam driver 904 , and a number of load cam rollers 74 .
- the cam driver 904 can be formed with a number of ramps 906 that are substantially similar to the ramps 106 .
- a plurality of magnetic elements 910 can be arranged and mounted on the traction ring 902 and/or the cam driver 904 . The magnetic force generated by an individual magnetic element 910 energizes the load cam roller 74 to tend to roll the cam roller 74 some distance up the ramp 906 to produce a minimum level of clamping force during operation of the CVT 50 . In other embodiments such as the one illustrated in FIG.
- a CFG 901 can include load cam rollers 974 and certain components of the CFG 900 .
- the load cam roller 974 can be a magnetic element so that the load cam roller 974 tends to attract and contact the traction ring 902 and the cam driver 904 .
- the load cam rollers 974 can be cylindrical rollers, barrel-shaped rollers, or spherical rollers.
- a CFG 950 can include a traction ring 952 , a cam driver 954 , and a plurality of load cam rollers 74 .
- a number of ramps 956 can be integral to the traction ring 952 .
- a second plurality of ramps 957 can be integral to the cam driver 954 .
- the ramps 956 and 957 are substantially similar to ramps 106 and cooperate with load cam rollers 74 to produce a clamping force during operation of the exemplary CVT 50 .
- a load cam roller cage 951 can retain the load cam rollers 74 .
- a group of tabs 960 can extend from the traction ring 952 at a substantially ninety degree angle from the side of the traction ring 952 having the ramps 956 .
- a second group of tabs 962 can extend at a substantially ninety degree angle from the cam driver 954 having the ramps 957 .
- the tabs 960 and 962 can be formed with flat or angled faces that are generally assembled to be in proximity to each other during operation. Typically, the tabs 960 and 962 are arranged to operate within slots of the load cam roller cage 951 . In some embodiments, the tabs 960 and 962 are formed on the outer diameter of the traction ring 952 and the cam driver 954 and can operate generally outside of the load cam roller cage 951 .
- a spring element 980 can attach to the tabs 960 and 962 , respectively. One end of spring element 980 can be attached to the tab 960 while the other end of the spring element 980 can be attached to tab 962 .
- magnetic elements can replace the spring element 980 and can be arranged to produce a resultant force that tends to direct the traction ring 952 away from the cam driver 954 .
- the spring element 980 can be a coil spring of the compression type, a scissor spring such as spring 611 , or wave spring, for example.
- a CFG 1000 can include a traction ring 1002 , a plurality of load cam rollers 74 , and a cam driver 1004 .
- a plurality of ramps 1006 with pockets 1006 P can be integral to the traction ring 1002 .
- the ramps 1007 can be integral to the cam driver 1004 and have pockets 1007 P.
- the load cam rollers 74 can be retained in a load cam roller cage 1008 , which can be substantially similar to load cam roller cage 76 , 108 , or 622 .
- slots 1009 provided in the load cam roller cage 1008 can also be used to retain a number of spacer elements 1010 .
- the load cam roller cage 1008 is provided with sixteen slots 1009 , eight of which retain load cam rollers 74 and eight of which retain spacer elements 1010 .
- the load cam roller cage 1008 can be provided with at least three slots 1009 , at least one of which retains a load cam roller 74 and at least one of which retains a spacer element 1010 .
- the spacer element 1010 can be a spring 1050 .
- the spring 1050 can be formed from flat spring steel that is known in the relevant technology.
- the width of the flat spring steel can be approximately equal to the width of the cam roller 74 and less than the width of the slot 1009 .
- the spring 1050 can be provided with a number of bends.
- the wave spring 1050 can be provided on one end with a bend 1052 and on the opposite end with a bend 1054 .
- the bends 1052 and 1054 are configured to contact, respectively, the pockets 1006 P and 1007 P.
- the spring 1050 can further be provided with retaining shoulders 1056 and 1058 that generally extend from the bends 1052 and 1054 .
- the retaining shoulders 1056 and 1058 can be adapted to be retained in the roller cage 1008 .
- a central portion of the wave spring 1050 can have a number of bends 1059 that give the wave spring 1050 elasticity.
- the elasticity of the spring 1050 allows, among other things, the spring 1050 to be compressed and inserted into the slots 1009 during assembly.
- the spring 1050 can be provided with only the bend 1054 , for instance in a configuration where the ramps 1006 are absent from the cam driver 1004 .
- a spacer element for a CFG 1005 A can be a wire spring spacer 1030 arranged in the slot 1009 of load cam roller cage 1008 .
- the CFG 1005 A includes a cam driver 1090 .
- the wire spring spacer 1030 can be a curved wire 1032 retained on one end in a housing 1034 .
- the housing 1034 can be made from plastic, for example, and be generally rectangular in shape with dimensions compatible With the dimensions of the slots 1009 .
- the curved wire 1032 is configured to extend from the housing 1034 and to contact the pocket 1007 P with a reaction surface 1036 .
- the wire spring spacer 1030 can be oriented so that at least one of the spacers 1030 is in contact with the ramps 1007 of the traction ring 1002 and at least one of the spacers 1030 is in contact with the ramps 1006 of the cam driver 1004 .
- a spacer element for a CFG 1005 B can be a wire spring spacer 1070 arranged in the slot 1009 of load cam roller cage 1008 .
- the wire spring spacer 1070 can be a curved wire 1072 retained in bore 1075 of a housing 1074 .
- the housing 1074 can be made from plastic, for example, and be generally rectangular in shape with dimensions compatible with the dimensions of the slots 1009 .
- the curved wire 1072 is configured to extend from the housing 1074 and to contact the pockets 1007 P and 1006 P with reaction surfaces 1076 and 1077 , respectively.
- the spacer element can be a spring loaded roller 1040 .
- the spring loaded roller 1040 can include a first hemi-cylindrical body 1042 and a second hemi-cylindrical body 1044 .
- the first hemi-cylindrical body 1042 can be provided with a pocket 1043
- the second hemi-cylindrical body 1044 can be provided with a pocket 1045 .
- the hemi-cylindrical bodies 1042 and 1044 can be coupled together by a spring 1048 .
- One end of the spring 1048 can be attached in the pocket 1043 while the other end of the spring 1048 can be attached in the pocket 1045 .
- the spring loaded roller 1040 can be arranged in slots 1009 formed in load cam roller cage 1008 .
- the arrangement of the spring loaded rollers 1040 can be similar to the arrangement described previously for the wire spring spacers 1030 ; however, it is preferably to use the spring loaded roller 1040 in embodiments where both the traction ring 1002 and cam driver 1004 have, respectively, ramps 1007 and 1006 . It will be readily apparent to a person having ordinary skill in the relevant technology that the spring load roller 1040 can be configured to accommodate cylindrical rollers, spherical rollers, or barrel-shaped rollers, for example.
- a CFG 1025 includes a spacer element that is a spring loaded plunger 1060 retained in the road cam roller cage 1008 .
- the spring loaded plunger 1060 can include a cylindrical sleeve 1062 adapted to enclose a spring 1064 .
- the spring 1064 surrounds a guide 1066 .
- a plunger 1061 can be coupled to one end of the spring 1064 and to the guide 1066 .
- the sleeve 1062 can enclose a portion of the plunger 1061 .
- the plunger 1061 can be provided with a foot 1068 that extends from the plunger 1061 to contact the pocket 1007 P.
- the foot 1068 can be formed with a toe 1069 that is generally conformal to the pocket 1007 P.
- the spring loaded plungers 1060 can be arranged in the load cam roller cage 1008 so that a number of the spring loaded plungers 1060 are in contact with the pockets 1006 P while a number of spring loaded plungers 1060 are in contact with the pockets 1007 P.
- a CFG 1035 can include a traction ring 1102 and a cam driver 1104 in contact with a plurality of load cam rollers 74 .
- the load cam rollers 74 can be retained in load cam roller cage 1108 .
- a number of wire springs 1110 can be attached to the load cam roller cage 1108 .
- the wire springs 1110 can be formed from metallic wire with a series of bends that form a generally U-shape structure having ends 1111 extending from a base 1112 . The ends 1111 can contact the traction ring 1102 .
- the base 1112 can clip to the load cam roller cage 1108 in such a way that the ends 1111 are positioned on each side of the load cam roller cage 1008 .
- the ends 1111 can have a plurality of bends that give the wire spring 1110 elasticity.
- wire springs 1110 tend to position the load cam roller cage 1108 with respect to the traction ring 1102 .
- the load cam roller cage 1108 engages the load cam rollers 74 so that they are positioned generally on the flat portion of the ramps 1106 .
- the cam rollers 74 can roll up the ramps 1007 for some distance to produce a preload to ensure that a certain minimum level of clamping force will be available during operation of the exemplary CVT 50 .
- a CFG 1500 included the traction ring 1002 and the cam driver 1004 in contact with a number of load cam rollers 601 .
- the load cam rollers 601 couples to the load cam roller cage 1008 .
- a number of wire clips 1550 couple to the load cam roller cage 1008 .
- a wire clip 1550 includes a series of bends that form an enclosing structure having a clip end 1506 , clip end 1505 , clip side 1508 A, and clip side 1508 B. More particularly, in some embodiments, the clip end 1506 is positioned perpendicular to the clip sides 1508 , and similarly the clip end 1505 is positioned perpendicular to the clip sides 1508 .
- the clip ends 1505 , 1506 can be positioned substantially parallel to one another and at distal ends of the clip sides 1508 .
- the clip sides 1508 are positioned parallel to each other, with the clip ends 1505 , 1506 positioned between the clip sides 1508 .
- the clip ends 1505 , 1506 and the clip sides 1508 are provided as a single, integral wire having the described clip ends 1505 , 1506 and the clip sides 1508 .
- the clip sides 1508 have at least one bend (for example, forming a generally “S” shape) that enhances the elasticity of the wire spring 1550 .
- the clip end 1506 is adapted to couple to the pocket 1007 P.
- the clip end 1505 is adapted to couple to the pocket 1006 P.
- the wire clips 1550 act to position the cam driver 1004 with respect to the traction ring 1002 .
- the load cam roller cage 1108 engages the load cam rollers 601 in such a manner that the load cam rollers 601 are positioned generally on the flat portion of the ramps 1006 and 1007 .
- the cam rollers 601 roll up the ramps 1006 and 1007 for some distance to produce a preload that ensures that a certain level of clamping force is during operation of the exemplary CVT 50 .
- a CFG 1600 includes a traction ring 1602 , a cam driver 1604 , and a load cam roller cage 1606 interposed between the traction ring 1602 and the cam driver 1604 .
- the load cam roller cage 1606 is adapted with a number of slots 1608 , each slot 1608 configured to receive a spring loaded ramp 1610 , a load cam roller 1612 , and a spring 1614 .
- the load cam roller cage 1606 additionally includes a central bore having a number of splines 1616 .
- the splines 1616 are preferably configured to engage mating splines (not shown) of a housing member of the CVT 100 .
- a CFG 1700 includes a load cam roller cage 1702 positioned between a traction ring 1704 and a load reaction ring 1706 .
- the load cam roller cage 1702 includes a flange having a number of cage splines 1708 .
- An input torque driver 1710 includes a number of driver splines 1712 configured to mate with the cage splines 1708 .
- the input torque driver 1710 can be coupled to the load cam roller cage 1702 by any other suitable ways.
- the load reaction ring 1706 is adapted to react loads transmitted between the traction ring 1704 and the input torque driver 1710 via a load cam roller 1714 , a spring loaded ramp 1716 , and a spring 1718 .
- the load reaction ring 1706 is rotationally fixed to the input torque driver 1710 , which can be accomplished with suitable coupling dowels, for example, between the input torque driver 1710 and the load reaction ring 1706 .
- the input torque driver 1710 includes a flange 1720 adapted to provide a guiding or receiving surface for the load reaction ring 1706 . It should be noted that the CFG 1700 configuration provides for a decoupling of the axial load reaction and the torque transfer.
Abstract
Description
Claims (20)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US13/765,409 US9086145B2 (en) | 2006-11-08 | 2013-02-12 | Clamping force generator |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
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US86494106P | 2006-11-08 | 2006-11-08 | |
PCT/US2007/023315 WO2008057507A1 (en) | 2006-11-08 | 2007-11-06 | Clamping force generator |
US51406209A | 2009-05-07 | 2009-05-07 | |
US13/765,409 US9086145B2 (en) | 2006-11-08 | 2013-02-12 | Clamping force generator |
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PCT/US2007/023315 Continuation WO2008057507A1 (en) | 2006-11-08 | 2007-11-06 | Clamping force generator |
US51406209A Continuation | 2006-11-08 | 2009-05-07 |
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US20130152715A1 US20130152715A1 (en) | 2013-06-20 |
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Also Published As
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US20100093485A1 (en) | 2010-04-15 |
EP2089642B1 (en) | 2013-04-10 |
US20130152715A1 (en) | 2013-06-20 |
US8376903B2 (en) | 2013-02-19 |
EP2089642A1 (en) | 2009-08-19 |
PL2089642T3 (en) | 2013-09-30 |
WO2008057507A1 (en) | 2008-05-15 |
TWI518270B (en) | 2016-01-21 |
TW200839127A (en) | 2008-10-01 |
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